Derricks



Aug. 25, 1959 H. J. TROCHE 2,901,125

DERRICKS Filed June 22, 1954 4 Sheets-Sheet 1 I3 13 15 W v3 n l l2 Flgil Fig.2

IN V EN TOR.

HE/P/I/l/M/ J. TEOCHZ MAW ATTO/P [Y Aug. 25, 1959 v H. J. TRocHE DERRICKS 4 Sheets-Sheet 2 Filed June 22, 1954 INVENTOR. Hf/PMA/V J T/POCH A rr /P/v Aug. 25, 1959 Filed June 22, 1954 H. J. TROCHE DERRICKS 4 Sheets-Sheet 3 Aug. 25, 1959 H. J. TROCHE DERRICKS 4 Sheets-Sheet 4 Filed June 22, 1954 INVENTOR. HEP/WAN J 7'/POC// United States Patent DERRICKS Herman J. Troche, Fairview Park, Ohio, assignor to J. Hf. alolan Corporation, Cleveland, Ohio, a corporation 0 hi0 Application June 22, 1954, Serial No. 438,436

8 Claims. (Cl. 212-8) The invention relates to derricks. Particularly, it relates to power-operated means for raising and lowering derricks from and toward inoperative stored position to and from working positions. These particular derrick erection means are an improvement over means for a similar purpose shown, described, and claimed in a pending application for patent on improvements in Derricks, Serial No. 413,097, filed March 1, 1954, by Herman J. Troche and George H. Eckels.

These improved derrick erection means will be referred to herein, whenever the context permits, as a link erector, and they are applicable to the standard type of derrick wherein the actual derrick work is efiected by the aid of a winch line, and the live boom type of derrick wherein the derrick can be elevated under load, all as fully described, insofar as the work operations of two types of derrick are concerned, in said pending application Serial No. 413,097.

The instant improved link erector is designed to be of general application in that it is installed and app1icable for use whether the derrick is being moved upwardly outboard by a winch-operated cable, or by a separate cylinder for actuating the center leg of a live boom type of derrick, or by the particular cylinder assembly forming part of the improved link erector mechanism herein shown and described. Inasmuch as the functions of certain parts of the instant link erector differ according to where force is applied to lift the derrick upwardly outboard, the reasons for these diiferent functions will appear hereinafter as they are described in detail.

For purposes of illustration only, the invention is described herein and shown in the accompanying drawings as applied to a standard type of derrick wherein the derrick is erected by the hydraulic cylinder forming part of the invention shown and described herein. However, what transpires during the erection and working of a derrick of the live boom type, and during use of a cable for lifting the derrick outboard, will also be described. This derrick of the instant application is shown as supported on the rear of the body of a utility truck from which the derrick efiects its work operations and upon the roof of which it is stored and transported when not in use. However, the improved link erector is applicable to derricks supported on many types of platforms or bases. Utility truck bodies and their equipment, including derricks, are utilized for many purposes, important amongst which is the installation and maintenance of the poles, lines, and other facilities of public utility companies, including a stiif leg operation of the derrick which is employed for stump pulling and equivalent operations.

The annexed drawings and the following description set forth in detail certain means exemplifying the improvements as applied to a standard type of derrick; such means constituting, however, only one of the various forms in which the invention may be embodied and only ice one .of the various types of derricks to which it may be applied. j

In said annexed drawings:

Figure 1 is a rear elevation of a utility truck body upon which is mounted a standard form of derrick having opposed upwardly converging side legs and a center leg, the derrick being shown in a high working position about beyond horizontal stored position, one of the improved link erectors being applied to each side Figure 2 is a fragmentary side elevation, taken from the plane indicated by the line 22, Figure 1, this view particularly showing the relative positions of certain link erector elements in the stated position of the derrick;

Figure 3 is a vertical elevation, partially in section, and upon an enlarged scale, taken from the planes indicated by the line 3-3, Figures 1 and 4, the view showing the right rear compartment of the truck body wherein various elements of the link erector applied to the right hand derrick side leg are contained, this right hand derrick side leg being shown in the position which it occupies on the roof of the truck body when the derrick is stored, and the elements of the link erector being shown in the relative positions which they occupy in the stored position of the derrick;

Figure 4 is a fragmentary plan view, taken from the plane indicated by the line 4-4, Figure 3;

Figure 5 is a fragmentary plan section, upon an enlarged scale, taken in the plane indicated by the line 5-5, Figure 3;

Figure 6 is a view similar to Figure 3, in which the derrick is shown as being in a working position substantially rearwardly of the derrick position shown in Figures 1 and 2, the derrick position of Figure 6 being about beyond horizontal stored position;

Figure 7 is a section of a socket member forming a mount for a derrick side leg, the view being taken in the plane indicated by the line 77, Figure 6;

Figure 8 is a view similar to the upper part of Figures 3 and 6, in which the derrick is shown in substantially extreme lowered position for reeving of the winch cable through the derrick head, this position being about from horizontal storage position of the derrick;

Figure 9 is a fragmentary plan section taken in the plane indicated by the line 9-9, Figure 8;

Figure 10 is an unassembled perspective of the elements of a control lever and mounting therefor for a certain oil pressure release valve; and

Figure 11 is a vertical section of the upper part of the frame assembly for the derrick link erector, showing the derrick in stored position, there also being shown by -dot-and-dash lines six stages of erection, at 30 intervals, and a winch line reeving position, 195, the eight dilferent derrick positions being indicated A, B, C, D, E, F, G, and H, respectively, the corresponding positions of a pivotal axis at the bottom of a link erector element being indicated by A, B, C, D, E, F, G, and H, respectively, and the corresponding positions of a pivotal axis at the top of such link erector element being indicated by A B C D E F G and H respectively.

Referring to the accompanying drawings in which the several structural parts are designated by the same respective numbers in the different views, a derrick having left hand and right hand similar and converging side legs -5 and 6, respectively, and a center leg 7, is mounted on the rear of a utility truck body .1. The body 1 has a supporting frame assembly 2 on each side at the rear, housing the operating mechanism for the derrick link erector, this frame assembly 2 having outside walls 2 and an inside closure formed by a wall 2 of the utility truck body 1, as shown in Figures 3, 5, and 6.

This link erector mechanism is the same for each of the derrick side legs 5 and 6, so only one link erector assembly will be described.

The side legs 5 and 6 are each secured at their bottom ends in a socket member which is a derrick mount pivotally secured to and at the rear of the body 1 somewhat above the level of the body roof 16, and the center leg 7 is pivotally and removably mounted in a bracket 11, Figures 1 and 2, on a rear body platform 4 at about the level of a center longitudinal body working floor 3. The center leg 7 has a telescoping lower section 8 serving to provide adjustable length for this center leg. Adjacent their tops all three derrick legs are so pivotally mounted in a common head 9 as to provide universal action as between the side legs 5 and 6, and the center leg 7, all as particularly shown and described in said pending application Serial No. 413,097. A storage position of the derrick on the roof 16 of the body 1 is shown in Figure 3, and two working positions and a winch line reeving position are shown in Figures 1, 6, and 8, respectively. A succession of derrick positions during erection, by 30 stages, is shown in Figure 11.

The leg-receiving portion of the socket member or mount 10 is provided with diametrically-opposed vanes or wings welded thereto and merging into an enlarged outer end longitudinally-extending plate 13 having a reinforcing rib 14, Figures 6 and 7. The plate 13 is pivotally mounted adjacent its outer end, Figures 1, 2, 3, 4, 6, 8, and 11, on a bolt 12 secured at its ends in spaced plates 17, Figure 4, which are erected on the tops of longitudinally spaced vertical channels 25 defining the front and rear of the supporting frame assembly 2. Reinforcing blocks 62, Figures 3, 6, and 11, are provided for the plates 17. The bottom edge of the plate 13 is formed intermediate its ends and on the inboard side of the vertical plane containing the axis 12 into a downwardly-projecting lug-like extension 18, Figures 2, 3, 6, 8, and 11, by which it is pivotally secured by pin 19 to the upper yoke end 38 of an erector link 31 of I-beam cross-section and hereinafter described. At the lower end of its outer edge, the plate 13 is provided with laterally-spaced blocks 24, Figures 3, 6, 8, and 11, adapted, as the plate 13 is turned to erect the derrick, to engage the body of the link 31 adjacent a lower pivotal axis 30 of the link 31.

The pivotal movements of the socket member or mount 10 and, hence, the erecting and storing movements of the derrick, are induced by a double-acting substantially vertically positioned hydraulic cylinder 20 pivotally mounted at its bottom end by an eye link 20 on an angle bracket 20' secured to a cross channel (not shown) at the bottom of the frame assembly 2, Figures 3 and 6. The cylinder 20 has a piston 21, a piston rod 21', an upper port 22, Figure 3, and a lower port 23, the ports 22 and 23 having restricted oil passages 22 and 23' respectively. The piston rod 21 has an upper eye part 21 Figure 5, pivotally mounted on the axis of the lower end of the link 31. A pin 30 providing the lower pivotal axis of the link 31 and having rollers 29 at its ends is mounted in the upper eye part 21 of the piston stem 21' and secured by set screws 33 to the spaced arms 32 of a lower yoke part of the link 31, Figure 5.

The link 31 is a rigid structure and of I-beam crosssection throughout the greater portion of its length and is drilled at a top yoke end portion 38 for accommodation of a pin 19 by which the link 31 is pivotally secured to the lug 18 of the socket plate 13.

The side wings 26 of that channel which serves as a front wall of the frame assembly 2, Figure 5, have rear inwardly-extended flanges 27. Adjacently within the forward part of channel 25 and abutting wings 26 are narrow vertical channels 28 whose inner flanges 35 extend upwardly substantially to the top of the plates 17 and extend a substantial distance downwardly adjacently interiorly of the channel 25 to a plane slightly above the cylinder 20. The outer flanges 35 of the channels 28 extend upwardly substantially to the plane of the upper end of the link 31, Figure 3, and form a straight guideway 36. These outer flanges 35' are welded at their top ends to arcuate rearwardly concave guideway channels 39 so that a complete inner vertical guideway wall is formed of the configuration shown in Figures 3, 6, and 8, and consisting of a straight vertical portion 36 and an arcuate vertical portion 36, the rear flanges 27 of the channel 25 serving as the outer wall 37 of guideway, as will now be more fully described.

The inside faces of the flanges 27 of the channels 25 forming the second and rear guideway wall 37 extend downwardly from a point substantially below the top of the plates 17 to the horizontal plane of the lower end of the front track section 36, and this rear track section or guideway wall 37 is straight, Figure 3, and opposed to the straight track section 36, and the lower portion of the arcuate track section 36.

It is evident that the structure thus far described provides for the lifting of the derrick side legs 5 and 6 from storage position, Figure 3, toward operating positions, Figures 1, 6, and 11, upon outward movement of the cylinder piston rod 21, the center leg 7, when detached at its lower end, hanging suspended from the head 9. Until the derrick reaches a position somewhat beyond position E, Figure 11, the rollers 29 at the bottom of the link 31 travel upwardly in the straight guideway part 36 between the flanges 27 and 35' of the respective channels 25 and 28, the leg socket member or mount 10 turning on the bolt 12, and the pin 30 and the lower end of the link 31 turning on the piston stem 21, and the upper end of the link 31 turning with the pin 19 in the lug 18. At this point, i.e., somewhat beyond the position E, Figure 11, the rollers 29, on further downward movement of the derrick legs, commence to travel in the curved portion 36 of the guideway. However, this curved portion 36' of the guidewayserves no function when the derrick is moving downwardly outboard, as will be hereinafter more fully referred to, the service provided by this curved guideway section 36' being effective during travel of the derrick inboard in a manner also hereinafter fully described. As the roller end of the link 31 emerges from the restricted portion 36 of the guideway to travel on the circular guideway 39, the blocks 24 on the socket plate 13 engage the link 31, Figure 6. The continuing movement of the plate 13 causes the upper link axis 19 to turn with plate 13 on pin 12 as a center and the rollers 29 travel in the longitudinally enlarged guideway area 36', the pivotal mounting of the hydraulic cylinder 20 permitting it and the piston rod 21' to move forwardly, as shown in Figure 6, which Figure 6 illustrates the respective positions after the derrick has moved further downwardly about 15 from the E position of Figure 11. The roller pivot end of the link 31 starts coming forward when the position D of the derrick leg shown in Figure 11 is reached. The continued rearward and downward movement of the derrick outboard carries the rollers 29 upwardly within the curved guideway channel 39 and the upper link pivot axis 19 downwardly, the desrick being capable of reaching an extreme lower winch line reeving posit-ion H, Figure 11, also shown in Figure 8.

Inasmuch as the movement of the derrick legs downwardly beyond vertical position D, Figure 11, does not require power and an oil pump 34, Figure 3, is running continuously, means are provided for the oil pressure to by-pass the cylinders 20, as hereinafter fully described. The derrick is prevented from falling outboard too fast of its own weight by the restricted passages 22' and 23' in the ports 22 and 23 of the cylinders 20 which provide slow controlled downward movement of the derrick. After the block 24 contacts the link 31, i.e., about 135, the fact that the oil cannot escape from the top of the cylinder 20 any faster than is permitted by the restricted port 22' prevents the derrick from falling too fast. Furthermore, when the outwardly moving derrick passes a position of about 110, the piston rod 21' acts as a tension member by reason of the oil pressure at the top of the cylinder 20 operating against the piston rod moving upwardly too rapidly.

The control means eifecting by-passing of the oil during downward outboard movements of the derrick are set to act at about 110 outboard from the storage position of the derrick. Such angular position is thus calculated in order to provide a safety factor of about twice the amount that would be required for the maximum grade of uneven terrain that could be practicably used for basing the utility body upon which the derrick is mounted. These control means comprise a cam 41 welded to a sleeve 40, Figures 3, 6, 8, and 11, which in turn is welded to the leg socket plate 13, this cam 41 engaging a roller 44 mounted on a pin 49 in an upper end yoke 42' of a release valve lever 42, Figure 10, pivotally mounted intermediate its ends on a shaft 43 welded to one of the plates 17, Figure 10. The lower end of the release valve lever 42 is formed with a flat face portion 45 which, when the cam 41 engages the roller 44 to swing the lever 42, moves a valve port control plunger 47, Figure 3, of a release valve 46 supported in a bracket 48, Figure 6, mounted on the frame assembly. This engagement of the plunger 47 by the face portion 45 of the lever 42 moves the plunger 47 inwardly of the valve 46 against the pressure of a spring 47 and opens valve ports (not shown) to by-pass the oil through the valve 46 instead of the oil taking its usual path into the bottom of the cylinder 20. There is only one release valve 46 and it is actuated by the movements of one of the plates 13, but suitable crosswise oil lines (not shown) are provided whereby the opening or closing of the valve 46 is properly reflected for oil movement in or oil movement shutoff from the bypass lines on both sides of the structure.

The oil under pressure is fed into the bottom of the hydraulic cylinder 20 to move the derrick outboard toward the rear. In other words, until the axes of the derrick side legs 5 and 6 reach somewhat beyond vertical position D, Figure 11, the upper link pivot 19 is moving counter-clockwise on its axis relative to the plate 13 but after the side legs 5 and 6 reach a position somewhat beyond the vertical position D, this upper link pivot 19 cannot so move but must move in unison with the plate 13. This results in the plate 13 directly moving the piston rod 21' against the resistance of the oil to being forced out of the cylinder 21), by reason of the restricted opening 22'.

During outboard movement of the derrick from its vertical position to a position of about 135, the holdback of the link 31 continues and the restricted opening 22 provides controlled downward movement of the derrick. Furthermore, derrick movement can be controlled by the manually-actuated handle 54, Figure 3, hereinafter mentioned.

normal flow of oil during derrick erection is from the pump 34 by line 63 into the bottom of a cylinder control valve 51, Figure 3, through the latter and out line 53 to port 23 at the bottom of cylinder 20. The return oil flows from cylinder 20 through port 22 at the top of cylinder 20 into line 52, thence into control valve 51, through the latter and out by line 58 to a reservoir 50, and back to the pump 34. The movement of the derrick toward storage position involves a reverse oil flow in which the oil is fed into the top port 22 of cylinder 20 and leaves by port 23. The control of the oil flow into and in, and out of the control valve 51 for various derrick manipulations is effected by various actuations of a plunger 56, Figure 3, by a pivotedhandle 54 connected pivotally to links 55 mounted on the body 1, all as fully shown and described in said pending application Serial No. 413,097.

When the outwardly moving derrick legs pass about the release valve 46 is opened and the oil from the left line 53 of the control valve 51, Figure 3, which normally passes to the bottom of the cylinder 20, passes through a line 59 to and through the release valve 46 and returns by line 60 to a port 61 of the tank 50. However, the vacuum created in the bottom of the cylinder 20, as the piston rod 21' moves upwardly, draws some oil into the cylinder 20.

When the derrick is retracted from an outboard position, the oil is fed into the right hand line 52 of the control valve 51, Figure 3, to the top port 22 of the double acting cylinder 20 and out the bottom port 23 of the latter. This return oil from the cylinder 20 can return to the reservoir 50 both by by-pass lines 59 and 60, and by valve line 53 until release valve 46 is closed due to the backward movement of cam 41 beyond roller 44, after which the oil returns to reservoir 54) by valve line 53 and valve 51 only. Again, as the derrick moves to storage position from vertical position, its descent is easy and controlled clue to the restricted passage 23' of the port 23 of the cylinder 20.

In a standard type of derrick the actual work operations are effected by the aid of a winch line 64 traversing a sheave 65 rotatably mounted in the upper end of the derrick center leg 7.

In the live boom type of derrick wherein for work operations the derrick can be elevated under load, i.e., either by a cylinder forming part of the center leg 7, or by cable action, instead of by the cylinders 20, the link 31 during rearward movement of the derrick is moved by the play of the side legs if there is uncontrolled movement between the side legs and the truck body. Thus, the link 31 then acts as a retarding member instead of a pushing member, and the track 33 guides the lower roller end of the link and keeps this end in its proper position. Since the outer end of the piston rod 21 is tied to the roller end of the link 31, this outer end of the piston rod is also kept in its proper path. In other words, during the return movement of the live boom type of derrick thus operated by means other than the cylinder 20, the concave Wall 39 takes the thrust and the rollers 29 engage and follow this wall 39 throughout its length. When this power means other than the cylinders 20 shown in the accompanying drawings and described herein causes an upward movement of the side legs, then a movement of the link 31 is also caused. The curved track section 39 provides a path that the roller end of the link 31 must follow during this movement. While the link 31 is thus following this movement it causes the piston 21' to telescope in the lift cylinder 20. On the other hand, for the return movement of the standard type of derrick or the live boom type of derrick wherein the work operations of the derrick are effected through the medium of the cylinder 20, there is a definite and material clearance all the way between the rollers 29 and the curved wall 39. Thus it is evident that the distinction between the different functions of the curved section 36' of the guideway is based on the different places at which the force to lift the derrick outboard is applied.

The value of the concave guideway track section 36' when operating with the standard type of derrick is obtained largely when the derrick is being used for a stiff leg operation, in which operation it is highly desirable that there be no disturbance of the truck setting. In fact, when the cylinder 20 is being utilized for work operations in the standard type of derrick other than stiff leg operation, the guideway could be dispensed with beyond thatv point therein corresponding to the point at which the blocks 24 have come into contact with the link 31. It is also evident that for difierent types of derricks, however erected and however operated for working purposes, the concave track section. 36' is serviceable only for derrick travel toward its transporting rested position from certain working positions within its range of movement. Thus, on a truck body loading operation with a live boom derrick over a limited range of 30 to 40, the aid of the concave guideway portion 36' is not required since during such operation the lower roller end of the link 31 is always travelling in the straight part 36 of the track. This 30 to 40 range of derrick movement for such loading operation is usually in a field from 10 to 20 outboard from vertical position of the derrick for picking up the load, to 20 to 30 inboard from vertical position of the derrick for depositing the load.

What I claim is:

1. A derrick, for use on a support upon which it is rested in lowered inboard position and is swingable through a sector of a circle between such inboard position and an outboard position, having converging side legs, a telescoping middle leg depending from the apex of the side legs and removably pivotally secured to the support, a cable playing over the derrick legs, mounts for the derrick side legs pivotally secured to the support, hydraulic means for erecting the derrick including a cylinder pivotally mounted on the support and having a piston and piston rod, means for controlling the hydraulic pressure, rigid linkage pivotally secured adjacent one end to the piston rod, the linkage being pivotally secured adjacent its opposite end to the respective mounts, abutments on and rigid with the respective mounts and engaging the linkage during movement of the derrick outboard, thus causing the linkage to turn with the mounts, and guideways for the piston rod and linkage mounted on the support.

2. A derrick, characterized as in claim 1, in which the guideways are formed to permit forward and rearward movements of the piston rod and the linkage during the derrick outboard movements.

3. A derrick, characterized as in claim 1, in which the guideways are formed to take the linkage thrust according to where the force is applied to lift the derrick upwardly outboard.

4. A derrick, characterized as in claim 1, in which the hydraulic pressure control means include restricted cylinder inlet and outlet ports.

5. A derrick, characterized as in claim 1, in which the guideways have rearwardly-concave portions, and in which, when the force for lifting the derrick outboard is applied outboard, the piston rod end of the linkage travels on said rearwardly-concave portions of the guideways during such outboard upward movements.

6. A derrick, characterized as in claim 2, in which the guideways are formed to confine the piston rod during any movements thereof between lower inboard derrick position and the derrick position obtaining when the linkageis engaged by the abutments.

7. A derrick, for use on a support upon which it is rested in lowered inboard position and. is swingable through a, sector of a circle between such inboard position and an outboard position for derrick erection and for cable-reeving from ground level, having converging supporting legs, a middle leg depending from the supporting legs and removably secured adjacent its lower end to the support, a cable playing over the converging ends of the supporting legs, a mount for each derrick leg pivotally secured to the support, hydraulic power means pivotallymounted on the support for erecting the derrick, such power means including a double-acting cylinder, piston and piston rod for each supporting leg, the cylinders being substantially vertically mounted and having restricted inlet and outlet ports, rigid links for the two mounts respectively pivotally secured adjacent their two ends to the respective mounts, and to the power means interiorly of the pivotal axes of the respective mounts, and abutments on the mounts adapted during the turning of the latter to engage the links adjacent their pivotal connections to the power means, thus causing the links to turn with the mounts, and guideways for the piston rods and links having upper-end rearwardly-concave portions formed to cause the links to act as retarding members during the upward movements of the derrick outboard.

8. A derrick, for use on a support upon which it is rested in lowered inboard position and is swingable through a sector of a circle between such inboard position and an outboard position, having converging side legs, a telescoping middle leg depending from the side legs and removably pivotally secured adjacent its lower end to the support, a cable playing over the derrick legs, mounts for the derrick side legs pivotally secured to the support, hydraulic means for erecting the derrick including a cylinder pivotally mounted on the support and having a piston and piston rod, means for controlling the hydraulic pressure, rigid linkage pivotally secured adjacent one end to the piston rod, the linkage being pivotally secured adjacent its opposite end to the respective mounts, the mounts being formed to engage the linkage during movement of the derrick outboard and cause the linkage to turn with the mounts, and guideways for the piston rod and linkage mounted on the support.

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